Circulating turbopump, particularly for central heating plants



May 24, 1966 J. L. STULENS CIRCULATING TURBOPUMP, PARTICULARLY FORCENTRAL HEATING PLANTS 4 Sheets-Sheet 1 Filed May 13, 1964 in i NN m y1966 i J. L. STULENS 3,252,422

CIRCULATING TURBOPUMP, PARTICULARLY FOR CENTRAL HEATING PLANTS Filed May15, 1964 4 Sheets-Sheet 2 May 24, 1966 J. STULENS 4 Sheets-Sheet 5 FiledMay 13, 1964 May 24, 1966 J. 1.. STULENS CIRCULATING TURBOPUMP,PARTICULARLY FOR CENTRAL HEATING PLANTS 4 Sheets-Sheet 4 Filed May 15,1964 7 3,252,422 QllRCULATlNG TURBOPUMP, PARTICULARLY FOR CENTRALHEATING PLANTS .lean Louis Stulens, 23 Rue du Tulipier,

. Brussels, Belgium Filed May 13, 1964, Ser. No. 367,166 Claimspriority, application Belgium, May 15. 1963, 506,393, Patent 632,364;Jan. 30, 1963, 516,033, Patent 643,173

18 Claims. (Cl. 103-97) My invention relates to circulating pumps(turbopumps), particularly for central heating installations.

It is known in central heating installations to use a circulating pumpbut that there is a difiicu-lty as regards the determination of thedirection of movement of the rotor.

A means frequently used is to provide an inspection window arranged soas to be able to check the direction of rotation of the motor from theoutside.

An arrow showing the direction of movement and a checking inspectionthrough the window do not however give complete security becauseexperience has shown that the arrow fixed or painted on the machine maygive rise to errors.

Furthermore, the inspection window is often soiled by impurities in thewater, particularly limestone and rust.

On the other hand, there are types of pumps with automatic priming whichpermit rotation in either direction, but when the direction of rotationis reversed, the direction of flow is likewise reversed, that is to saythe suction side becomes the delivery side.

Now the fact must not be overlooked that any element for providing acirculation (e.g. pump, agitator) can be driven by a single-phaseelectric motor or by an internal combustion engine, which implies inthis case one direction of circulation only and requires a specialturbine for each case, because of the great difliculty in adaptinginternal combustion engines to direct coupling.

Whenever a circulation-providing member is placed in a pump-connectingsystem or installation, it is impossible to avoid checking the directionof rotation. If the direction of rotation of the turbine should bereversed and if the electric current is three-phased, it is sufficientto reverse two phases, but for the single-phase or internal combustionengine the turbine has to be replaced in order to avoid danger of theflow being opposed to that of the thermosiphon. For instance, in thecase of heating the circulation may be stopped or a considerable brakingeffect may occur and may lead to an overheating of the water in theboiler.

An object of this invention is to overcome these ditficulties and inparticular to avoid the use of an inspection window.

The invention is also directed to obviating certain disadvantages andcertain difficulties connected with the present system involving aby-pass, which become neces sary because if this latter is omitted thecirculation may be stopped.

Known by-pass devices comprise a tapping which is completely separateand independent; such an arrangement is expensive, necessitates at leastthree valves and gives rise to difficulties because frequently the spacerequired is not available.

Gear pumps are also known and self-priming pumps provided with aseparate 'by-pass connected to a safety valve or a pipe for dischargingoverpressures are known, but these systems are very different in designfrom that which is the basis of the invention.

In short, the impurities in the water cause a blockage United StatesPatent 3,252,422 Patented May 24, 1966 of the rotor of the motor whichmakes it necessary to dismount the fittings.

If there is no bypass the installation has to be stopped and emptied andif there is a by-pass exteriorly to the appliance the cost isconsiderably increased and more space is required;

According to the invention there is provided in the frame-work of thepump a passage forming a by-pass (incorporated .by-pass) between thefluid entry side and the turbine outlet side and also a system of valvesin which a double-acting valve actuated from outside the framework ofthe pump can occupy two positions: one in which it is in contact with aseating situated at the entry to the turbine and the other in which itis in contact with a seating provided at the entry of a by-pass, while asecond valve also actuated from outside the framework co-operates with aseating provided at the outlet or delivery side of the turbine.

The invention will next be described in conjunction with the attacheddrawings, wherein:

FIGURES 1 and 2 are views in vertical section showing the framework ofthe pump and also the turbine and the motor, the valve systems being intwo different positions;

FIGURES 3 and 4 are sections along lines IIIIII and IVIV in FIG. 1; and

FIGURES 5 to 10 are diagrammatic views of variants of the form of theblades.

In FIGURE 1 is shown a turbine consisting of two flanges 1 and 2 withone of which the inlet body 3 of the turbine is integral, which rotatesin a sleeve 4 (FIG- UR E 1) forming part of the framework 5 of the pump,

while the other flange 2 carries the socket 6 which is keyed on theshaft 7 of the motor 8 fixed to the framework by bolts 9.

In accordance with the invention the blades P are of a special form inthat they comprise (FIGURES 7 and 8) two profiles which are symmetricalin relation to the 1ongitudinal axis of the blade, in such a way thatthe turbine is double-acting, that is to say that whatever the directionof rotation the direction of flow of the liquid remains unchanged.

In such a machine no inspection window is necessary because it deliversequally well in either direction while preserving the same direction offlow of the fluid.

Such a feature is therefore applicable to any machine used for moving afluid.

As shown in FIGURES 1 and 2, in the framework 5 of the pump there isprovided between the fluid entry side and the outlet side a passage 10forming a by-pass, and a valve 11 is provided which is actuated by a rod12 provided with a control wheel 13 and which can occupy two positions;one in which the valve is in contact with the seating formed by thesleeve 4 at the entry of the turbine and the other in which it is incontact with a seating or sleeve 14 provided at the entry of theincorporated by-pass '10.

A second valve 15 actuated by a rod 516 provided with a control wheel:17 co-operates with a seating d8 provided at the outlet '19 ordischarge point of the turbine.

When the doubleaacting valve 11 is in the position shown in FIGURE 4,that is to say is in contact with the seating 14, and if the valve 15has been opened, circulation takes place forced by the turbine, as shownby the arrows in FIGS. 1, 3 and 4.

When these valves are in the position shown in FIG- URE 2, with thevalve 15 closed and the valve 1 1 in contact with the seating 4 (that isto say closure of the suction side of the turbine) the passage 10 actsas a by-pass permitting free and direct flow, which makes it possible todismount the motor and the turbine without other precautions having tobe taken while the installation continues to act as a thermosiphon.

By opening the valves, the thermosiphon circulation ceasesautomatically, and forced circulation through the turbine isre-established.

An arrangement such as that shown in FIGURES 1 and 2, making possible astraight-line circulation in the pipeline, gives rise to an assemblywhich permits a considerable saving in labor and material.

These advantages may be summarized as follows:

( 1) Less space required.

(2) Simpler construction, fewer tappings, less welding and less risk.

(3) Very simple and easy mounting.

(4) In case of repair the motor and turbine can be dismounted withoutany other precaution than that of closing the valves.

(5) The dirt trap chamber can be rinsed out without dismounting.

(6) By arranging the handwheels'13 and 17 as shown and by giving themsuitable dimensions the risk of error in operation is avoided, becausebefore applying the valve 15 on its seating 18, that is to sayobstructing the turbine outlet 19, it is necessary to apply the valve 11on its seating 4; there is no risk therefore of closing the by-pass 10and at the same time obstructing the turbine outlet, which would stopthe circulation of water in the piping, could cause this water to boiland could therefore seriously damage the plant. Vice versa, beforeapplying the valve 11 on the seating 14 and therefore obstructing theby-pass 10, it is necessary to open the valve 15, which avoids thedrawback mentioned above. It would therefore be impossible to apply thevalve 11 on the seating 14 without first of all opening the valve 15,removing it from the seating 18. On the other hand if in error the valve11 is brought on the seating 4, while it has been forgotten to move thevalve 15 to bring it into contact with the seating 18, the by-pass wouldfunction normally and in the case of dismounting of the motor and of theturbine, the oversight would be quickly noticed because water would thenflow through the by-pass at the level of the turbine discharge point andat this moment it would become necessary to close the valve 15, to bringit on to its seating 18.

According to the invention, means are provided such that the liquid canbe discharged as freely as possible, and to obtain a better balance ofthe turbine and also a better distribution of wear of the bearing, andfor this purpose there is mounted on the motor shaft a balance componentwhich is locked between the motor and the pump framework and whichcomprises a peripheral recess extending to a position near the turbinesocket and communicating with the outlet and in the framework of thepump is provided a circular cavity arranged in such a way as to providea communication between the spaces between the blades and the recess inthe balance component.

For this purpose on the socket 6 carried by the shaft 7 of the motor ismounted a balance component which is positioned between the motor 8 andthe framework 5 of the pump. The component 20 has a peripheral recess 21extending to a position near the socket 6 of the turbine andcommunicating with the outlet 19.

On the other hand, in the framework 5 of the pump is provided a circularcavity 22 which is arranged so as to provide a communication between thespaces 23 between the blades P and the recess 21 in the component 20.The result is that the liquid which might tend to accumulate in thespaces 23 between the flanges 1 and 2 and the blades P, finds adischarge outlet through the cavity 22, the recess 21 and the dischargepoint.

It will be understood that this discharge can thus be effected morefreely and that the turbine is thus better balanced,

This component 20 is provided on the motor side with a slot 25 which isconnected through holes 26 with the recess 21 in such a way as to permitthe circulating fluid to lubricate and cool the motor 8 with suflicientpressure.

In the slot 25 is provided a filter 27, of felt, for example, to preventthe passage of solid particles.

As will be understood, it is possible to obtain two different rates offlow as requisite and according to the direction in which the turbine isrotating.

It will then be suflicient to calculate and to design the profile of thebladings in an asymmetrical manner corresponding to each of the tworates of flow.

The thickness of the blade can for instance be greater on the side ofthe entry flange 1 than on the side of the rear flange 2.

This difference is shown in FIGURES 6 and 8 at a selected point by e ande The edges 25 of the blades (FIGURE 6) are therefore inclined at anangle a, for instance 15 to the perpendicular connecting the flanges.

As shown in FIGURE 9, the number of blades may be more than three andmay be any number, for instance five.

On the other hand, the blade may be asymmetrical in relation to a radius(FIGURE 10) in order to have a given rate of flow for one direction ofrotation and another rate of flow for the other direction of rotation.

There can be provided through the rod 12 of the valve 11 a bore 28(FIGURES 1 and 2) which permits the insertion of a screwdriver which canengage in a slot 29 in the shaft 7 of the motor which enables the motorto be set in operation when first starting.

When the valves 11 and 15 are in the position in FIG- URE 2, if theoperator only unscrews the fixing nut 30 of the control handwheel 13 ofthe valve 11 to introduce a screwdriver through the bore 28 and to reachthe slot 29, the rotor can be unkeyed at any moment of operation of theinstallation without any serious danger of obstructing the circulation,because by closing the valves the forced circulation is cut and theby-pass is automatically opened with direct passage and only a few dropsof water will emerge at the moment when the nut 30 is removed. As soonas the rotor is unkeyed and the motor therefore in operation, the twovalves are brought back into the forced circulation position, but onlyafter putting the nut 30 back into place.

As an additional advantage, it is thus possible to obtain any desiredsetting of the rate of flow, because by bringing the valve 11 into aposition slightly displaced from the seating 14 a very sensitiveregulation of the rate of flow is obtained.

What I claim is:

1. A circulating pump comprising a framework and a turbine supported forrotation in the latter, said framework having an inlet for passage offluid to the turbine and an outlet for passage of fluid from theturbine, said framework further having a by-pass passage between thefluid inlet and the outlet, externally operable doubleacting valve meanssupported in said framework and operable between two positions in one ofwhich the by-pass passage is opened and the turbine inlet is closed andin the other of which positions the by-pass passage is closed and theturbine inlet is opened, and externally operable second valve meanssupported in said framework for selectively opening and closing saidoutlet, said valve means by virtue of their support in the frameworkbeing effective to directly act on the inlet and outlet of the turbineas well as on the by-pass passage.

2. A circulating pump according to claim 1 comprising a motor supportedon said framework and driving said turbine, the pump further comprisinga balance component which is locked between the motor and the frameworkand provided with a peripheral recess communicating with the outlet ofthe turbine, said framework being provided with a circular cavityproviding communication between the turbine inlet and the recess of thebalance component.

3. A circulating pump according to claim 2 wherein the balance componentis provided on the motor side with a slot connected by holes withtheperipheral recess of the turbine to permit the circulating fluid tolubricate and cool the motor with sufficient pressure.

4. A circulating pump according to claim 3 comprising a filter in saidslot in the balance component.

5. A circulating pump according to claim 1 wherein said turbine hasblades with two profiles which are symmetrical in relation to thelongitudinal axis of the blade such that whatever the direction ofrotation of the pump, the direction of flow of the liquid is the same.

6. A circulating pump as claimed in claim 5 wherein said blades have anasymmetrical shape to obtain two different rates of fluid flow for thedifferent directions of pump rotation.

'7. A circulating pump according to claim 5 wherein said turbine has anentry flange and a rear flange, the thickness of the blade being greateron the side of the entry flange than on the side of the rear flange.

8. A circulating pump according to claim 7 in which the edges of theblades are inclined at an angle of about 15 between the flanges.

9. A circulating pump according to claim 1 wherein said first valvemeans has a rod in which is provided a bore which permits the insertionof a screwdriver which can engage a slot in a shaft of a motor whichdrives the turbine to permit the setting in operation of the motor whenfirst starting.

10. A circulating pump comprising a framework and a turbine supportedfor rotation in the latter, said framework having an inlet for passageof fluid to the turbine and an outlet for passage of fluid from theturbine, said framework further having a by-pass passage between thefluid inlet and the outlet, said by-pass passage having an inlet whichis opposed to the turbine inlet, a valve supported in said framework andoperable externally thereof for movement between a first position inwhich the inlet to the by-pass passage is closed and the turbine inletis open and a second position in which the turbine inlet is closed andthe inlet to the by-pass passage is open, and a second valve which issupported in said framework and is operable externally thereof forselectively closing the turbine outlet.

11. A circulating pump as claimed in claim 10 wherein said valves areoperatively associated with one another such that said turbine outletcan be closed by the second valve only after the first valve has closedthe turbine inlet and opened the inlet to the by-pass passage, whereassaid turbine inlet can be opened only after the turbine outlet has beenopened by said second valve.

12. A circulating pump as claimed in claim 11 comprising control rodsfor said valves and wheels on said rods, said rodshaving differentlengths whereby said wheels are associated with one another such thatsaid turbine outlet can be closed by the second valve only after thefirst valve has closed the turbine inlet and opened the inlet to theby-pass passage, whereas said turbine inlet can be opened only after theturbine outlet has been opened by said second valve.

13. In a motor and impeller assembly in a liquid circulating system: aframework having a liquid inlet and a liquid outlet, the impellercomprising two spaced flanges one of which includes an integral inletbody portion, a sleeve in said framework and in which said inlet bodyportion is rotatably supported, means for securing the motor to theframework, a socket keyed to the motor for rotation therewith andcarried by the second of said flanges, said framework defining a passageforming a bypass between the liquid inlet and the liquid outlet, saidby-pass having an inlet and an outlet, a first seating disposed at theinlet body portion of the impeller, a second seating disposed at theinlet of the by-pass, a double acting valve actuated from outside theframework and adapted to occupy two positions, one in which it is incontact with the seating at the inlet of the by-pass and the other inwhich it is in contact with the seating at the inlet body portion of theimpeller, said impeller having a liquid outlet, a third seating at theoutlet of the impeller, a second valve also actuated from outside theframework and adapted to contact said third seating such that when saidfirst valve is in contact with said second seating and the second valvehas been opened, circulation takes place through said impeller, whereaswhen the second valve is in contact wtih the third seating and the firstvalve is in contact with the first seating the by-pass passage permitsfree and direct liquid flow therethrough which enables dismounting ofthe motor and of the impeller while the circulation continues to act asa thermosiphon.

14. In an assembly according to claim 13, in which a balance componentis disposed between the motor and the framework and is coupled to themotorin driving relation, said motor including a drive shaft, saidimpeller including a hub mounted on said drive shaft coupled to saidsecond flange, and spaced blades between and secured to said flanges,said balance component having a peripheral recess extending proximatethe hub of the impeller and communicatingwith the impeller outlet, saidframework being provided with a circular cavity which is arranged toprovide permanent communication between the spaces between the impellerblades and the recess in the balance component.

15. In an assembly according to claim 14, in which the balance componentis provided with a slot facing the motor and has holes extending betweensaid slot and said peripheral recess whereby the circulating fluid isadapted to cool and to lubricate the motor.

16. In an assembly as claimed in claim 13 wherein a filter is disposedin said slot in the balance component for filtering the circulatingfluid used for cooling said motor.

17. In an assembly according to claim 13, in which the blades have athickness which is greater in a region adjacent said one flange comparedto that adjacent the other flange.

18. In an assembly according to claim 13, in which the blade isasymmetrical in relation to a radius of the impeller so as to have agiven rate of flow for one direction of rotation and another rate offlow for the opposite direction of rotation.

7 References Cited by the Examiner UNITED STATES PATENTS 983,137 1/1911Heald 103-103 1,105,808 8/1914 Macneill 103112 1,829,122 10/1931 Wade103103 2,235,706 3/1941 Hanus 230114 2,779,290 1/1957 Wiegers 103393,135,211 6/1964 Pezzillo 10387 FOREIGN PATENTS 57,124 6/ 1891 Germany.

ROBERT M. WALKER, Primary Examiner.

1. A CIRCULATING PUMP COMPRISING A FRAMEWORK AND A TURBINE SUPPORTED FORROTATION IN THE LATTER, SAID FRAMEWORK HAVING AN INLET FOR PASSAGE OFFLUID TO THE TURBINE AND AN OUTLET FOR PASSAGE OF FLUID FROM THETURBINE, SAID FRAMEWORK FURTHER HAVING A BY-PASS PASSAGE BETWEEN THEFLUID INLET AND THE OUTLET, EXTERNALLY OPERABLE DOUBLEACTING VALVE MEANSSUPPORTED IN SAID FRAMEWORK AND OPERABLE BETWEEN TWO POSITIONS IN ONE OFWHICH THE BY-PASS PASSAGE IS OPENED AND THE TURBINE INLET IS CLOSED ANDIN THE OTHER OF WHICH POSITIONS THE BY-PASS PASSAGE IS CLOSED AND THETURBINE INLET IS OPENED, AND EXTERNALLY OPERABLE SECOND VALVE MEANSSUPPORTED IN SAID FRAMEWORK FOR SELECTIVELY OPENING AND CLOSING SAIDOUTLET, SAID VALVE MEANS BY VIRTUE OF THEIR SUPPORT IN THE FRAMEWORKBEING EFFECTIVE TO DIRECTLY ACT ON THE INLET AND OUTLET OF THE TURBINEAS WELL AS ON THE BY-PASS PASSAGE.